Machine functioning as a pump or a turbine and consisting of a mechanism transmitting rotational inertial forces of the periodic type to a tubular circuits system

ABSTRACT

The invention described in FIG.  1  of  4  concerns a hydraulic machine based on the utilization of the rotational inertial forces developed by 2 pairs of circuits (C 1 ,C 2 ) and (C 3 ,C 4 ) fastened respectively to the rotor R 1  and R 2.    
     Each rotor is subjected by a connecting rod-crankshaft system to an oscillatory motion of identical frequency and phase different from 180°. In operation as a pump the circuits (C 1 ,C 2 ) are respectively utilized in the rightward θ(0°,90°) and leftward θ(180°,270°) phases of the oscillatory motion of R 1 ; while the circuits (C 3 ,C 4 ) are respectively utilized in the rightward θ(0°,90°) and leftward phases θ(180°,270°) of the oscillatory motion of R 2 .  
     Operation of the machine as a turbine is characterized by rightward operation θ(90°,180°) of C 1 , leftward of C 2  in θ(270°,360°); rightward of C 3  in θ(180°,270°) and leftward of C 4  in θ(0°,90°). The power developed by the machine can be considerably increased by extending the active circuits as set forth below.

This invention relates to a machine functioning as a pump or a turbine and consisting of a mechanism transmitting rotational inertial forces of the periodic type to a tubular circuits system in accordance with the classifying part of claim 1.

Known machines of this type have not heretofore been developed for optimal performance.

The general purpose of this invention is optimization of machines of this type.

This purpose is achieved by a machine functioning as a pump or as a turbine and consisting of a mechanism transmitting to a system of tubular circuits rotational inertial forces of the periodic type in accordance with the characterizing part of claim 1.

The machine consist of the following components (see FIG. 1 of 4).

-   -   a. A shaft of the crank a_(ma) rotating on bearings fastened to         the supporting frame which by means of two cranks m_(ai) and two         connecting rods b_(i) imposes on the two rotors R_(i) an         oscillatory movement of equal frequency and different phase of         180°;     -   b. two pairs of tubular circuits C_(ij) fastened respectively to         R_(i) with inlets E_(ij) and outlets U_(ij) where i,j=1,2,3,4,         connected respectively to the inlet E_(o) and with outlet U_(o)         of the;     -   c. four pairs of valves V_(1.2) and V′_(1.2) each inserted in         the respective ends of C; and     -   d. the mechanical opening and closing device of each pair of         valves with Δθ=90° so as to determine the interval of conduction         with constant direction from E_(uj) toward U_(uj) of the mass         contained in the circuits C_(ij) as required by operation of the         machine as pump or as turbine.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows a diagram of the components necessary for operation of the machine;

FIG. 2 shows the shaft of the cranks a_(ma);

FIG. 3 shows a valve with mechanical control for opening and closing depending on the motion of the rotors R₁ and R₂.

FIG. 4 shows a valve.

DETAILED DESCRIPTION OF THE DRAWINGS

FIG. 1 of 4 shows the diagram of the components necessary for operation of the machine. Therein the two rotors R₁ and R₂ oscillate in the interval φ (+φ°,−φ°) around two parallel axes 00₁ and 0′0′₁ with the same frequency and different phase of 180°. Oscillation can also be done around a single shaft with the same interval. Oscillation equal and opposite to R₁ and R₂ is generated by rotation of the shaft of the cranks a_(ma) (see FIGS. 2/4) to which the two cranks m_(ai) of equal length are directly connected. The cranks transmit oscillatory motion to the two rotors by means of the respective connecting rods b₁ and b₂.

In the figure are shown the barycentric axes of the two circuits C₁ and C₂ fastened to the rotor R₁ and of the two circuits C₃ and C₄ fastened to the rotor R₂. Each circuit is curved in accordance with a semicircumference of barycentric radius r_(b) fastened to the corresponding rotor.

An identical valve with simultaneous opening and closing is inserted at the two ends of each circuit C_(ij). This is to establish the maximum independence from the other circuits and facilitate operation of the machine both as pump and as turbine.

Each circuit has an identical cross section S_(cl), identical length l_(ci)=NI_(b) and identical mass m_(c). The mass can be liquid, pasty or solid-broken up.

FIG. 1 of 4 has the following characteristics.

-   -   —the rotation axes 001 and 0′0′1 of the two rotors R₁ and R₂ and         the axis of the shaft of the crank a_(ma) are parallel; —the two         cranks m_(a1) and m_(a2) fastened to a_(ma) are equal and         opposite and the rotation angle θ of m_(a1) coincides with the         rotation angle θ of a_(ma); —for θ=0° the angle φ of rotation of         R₁ is null; —in addition for θ=0° the axes of the two connecting         rods b₁ and b₂, the axes of the cranks m_(a1) and ma2 and the         axis of rotation of a_(ma) belong to a plane parallel to that of         the axes of the two rotors; in addition the angles of rotation         of R₁ and R₂ are respectively (φ_(o)=0° and (φ=180°.

The maximum rotation angle φ_(o) satisfies the following relationship. (1) senφ_(o)=m_(a1/ro), where r_(o) is the radius of the connecting rod small end. From the relationship (1) is deduced the maximum rotation angle φ_(o) of R_(i); the angle φ can be expressed with good approximation by the relation (2) φ=φ_(o)sen θ, which is satisfied for the two ends θ=0° and θ=90°. Deriving the (2) as regards θ it is deduced that the angular velocity of R_(i) is (3) {dot over (φ)}=φ_(o) {dot over (θ)} cos θ; from which one has the angular velocity of the circuit expressed by (4) v_(o)=r_(b){dot over (θ)}; φ_(o) cos θ; it represents the velocity of the containing tube, or the greater relative velocity of the contained mass. In the hypothesis {umlaut over (θ)}=0, one has from (4) the angular acceleration (5) {umlaut over (θ)}=−φ_(o){dot over (θ)} senθ from which results the inertial force applied to the mass m_(c) (6) f₁=−m_(c)r_(B){umlaut over (φ)}=÷m_(c)φ_(o)r_(B){dot over (θ)}senθ.

From (4) and (6) is deduced the power developed by f₁ and by v_(c) in each circuit c_(i) expressed by (7) P_(c) _(i)=m_(c)φ² _(o)r_(B) ² {dot over (θ)}³ cos θsenθ, whose sign is equal to the sign of the cos θsenθ product.

It is observed that: a) a mechanical device (see below) imposes in Δθ=90° simultaneous opening of the two valves arranged at the two ends of each active circuit; therewith is established the interval of circulation of the mass contained therein; b) in the operation of the machine as indicated above, two circuits act simultaneously, of which one is fastened to R₁ and the other to R₂ with opposite orientation direction; This implies doubling the power and complete balancing of the machine; c) the length 1 _(c)=Π r_(b) of each circuit can be increased with the addition of N_(o) circumferences so that the mass contained in each C_(i) becomes m_(c)=n (1+2 N_(o)) r_(B) S_(c) p_(i).

The machine of FIG. 1 of 4 operates as a pump subjected to the inertial force developed by the oscillatory motion of the two rotors.

The same machine also operates as a turbine; applying to the input E_(o) the liquid subjected to the pressure f_(0T)/S_(c) developed by the external force f_(0T). Said pressure is distributed, as explained below, to each circuit.

In both cases the machine subject to oscillatory motion develops in each circuit the same inertial forces as above.

FIG. 2 of 4 shows the shaft of the cranks a_(ma) which transmits to the circuits c_(i,j) mechanical energy from an external motor for operation of the machine as a pump or transmits to the user the hydraulic energy taken from the machine operating as a turbine.

In both cases the energy is transmitted using the following series components: the shaft of the cranks a_(ma) connected to the two cranks m_(a1) and m_(a2) connected to the connecting rods b₁ and b₂ connected to the rotors R₁ and R₂ each connected to the respective active circuits C₁, C₂ and C₃, C₄ connected to the external sources.

FIG. 3 of 4 shows a valve with mechanical control for opening and closing, which depend on the motion of the rotors R₁ and R₂. The FIG illustrates the following components: a) a disk 1) fastened to a shaft 2) whose axis coincides with a diameter of the disk; b) two bearings 3) fastened to the tube 4), around which the shaft 2) can rotate; c) two toothings fastened to the ends of the shaft 2) which, with variation of the rotation angle of the rotor R_(i), couple with a rack fastened to the supporting frame causing 90° rotation of the disk, which causes opening or closing of the valve as required by operation of the machine.

The valve described has the advantage that in it the momentum applied to the axis 2) is always null and generated by a result of parallel forces applied to the axis of the disk.

In FIG. 4/4 is shown a valve consisting of, a) a tube whose interior has the form of a parallelepiped P_(r1) with rectangular cross section a₁×b₁ and height h₁; the liquid can run through the tube in accordance with the direction shown; b) a closing and an opening of the valve performed by a parallelepiped P_(r2) having rectangular cross section a_(o)×b₀ and height h_(o); rotation of P_(r2) is possible inside of P_(r1) around its side b_(o) parallel to b_(i) since b_(o)=b₁−ε where ε is the tolerance necessary and sufficient so that P_(r2) might rotate inside P_(r1); c) a rotation shaft a_(r) fastened to P_(r1) with axis parallel to the side b_(o); a_(r) is also fastened to the opposite plane of P_(r1) so that 1) P_(r2) might rotate inside of P_(r1) with maximum rotation α=A sin(a_(i)/h_(o)) where α is the closing angle of the valve; 2) for α=0 let P_(r2) be completely contained inside of P_(r1); therefore, for α=0, the cross section of the tube a_(i)×b_(i) is constant and the valve has no hydraulic losses due to its opening and closing organs.

B) SUMMARY OF THE OPERATION OF THE MACHINE

From the foregoing the following quantities result as a function of the angle θ of rotation of the crank shaft.

-   -   1) φ=φ sin θ which expresses the rotor oscillation angle;     -   2) φ=φ_(o)θ cos θ which expresses the rotatory velocity         (angular) of the rotor as a function of θ;     -   3) φ=−φ_(o)η²sen²θ which expresses the angular acceleration of         the rotor as a function of θ;     -   4) v_(c)=φ_(o)r_(b){dot over (θ)} cos θ which expresses the         velocity of the mass contained in the active circuit;     -   5) f₁=m_(c)φ_(o)r_(B) (dθ/dt) senθ which expresses the inertial         force applied to the mass m_(c) contained in c_(i).     -    From 4) and from 5) one deduces the value of the instantaneous         power developed by the active circuit:     -   6) P_(c)=v_(c)f₁=m_(c)φ_(o) ²r_(B) ²(dθ/dt)³senθ cos         θ=m_(o)φ_(o) ²r_(B) ²θ³senθ cos θ.

The value of P_(c) is positive for senθ cos φ>0 that is for θ included in the interval θ(0°, 90°) and θ(180°, 270°) in which the machine operates as a pump; while the machine operates as a turbine in the intervals θ(90°, 180°) and θ(270°, 360°) in which it is senθ cos θ<0.

The corresponding opening and closing values, designated byθ_(A) and θ_(c) of the above-indicated intervals, which are satisfied by the four active circuits in the operation as pump and as turbine, are deduced.

They are set forth in the following table where S=counter-clockwise and D=clockwise. PUMP TURBINE C_(i) θ_(A) θ_(c) V_(c) f_(c1) C_(i) θ_(A) θ_(c) V_(c) f_(c1) C₁   θ°  90° S S C′₁ 90° 180° S S C₂ 270° 180° D D C′₂ 270°  360° D D C₃ 180° 270° D D C′3 270°  360° D D C4  90°  0° D D C′4 90° 180° S S

Integrating 6) in θ(0°, 90°) one deduces the power developed by C₁ at θ(0°, 90°). P _(c1)=1/n m _(oφ) _(o) ² r _(B) ²(dθ/dt)³

The machine consists of four identical circuits of which only two operating in the same interval. Therefore it is deduced that the power developed by the machine is as follows. P _(o)=4 P _(c1)=(4/Π) m _(c) φ_(o) ² r _(B) ² (dθ/dt)³ From the foregoing it is deduced that operation of the machine is based on use of the two following forces.

-   -   rotational force f_(R)=m_(c)r_(B){umlaut over (φ)} where {umlaut         over (φ)} is the angular acceleration of the rotor R₁; it         generates the hydraulic power P_(o1)=f_(R) V_(c1);     -   inertial force f₁ which uses for connection the series of         components R₁, b₁, m_(a1) and Q_(ma) and generates an equal and         opposite mechanical power at P_(oi).         In this manner, exchange of the hydraulic power generated by the         active circuits with the mechanical power of the crankshaft is         performed.

The value of the power developed by the machine in operation as pump and as turbine is of absolute equal value and contrary sign.

The variation in operation as pump or as turbine involves substitution of the intervals indicated in the above table. It is important to note that each pair of intervals has the following characteristics: a) each has a point in common; b) substitution therefore involves only variation of a closing point and construction of another point; c) the two pairs have a velocity of the liquid of mean constant value and inertial force of contrary direction.

C. ADVANTAGES OF THE MACHINE

The machine has the below-listed advantages.

1) High output due to the absence of dissipative components such as directional blades or impellers with blades and pistons. The eight valves used in it have negligible losses since they are operated in the absence of liquid conduction and because their cross section after opening is practically identical to that of the conduction tube and because each one operates only for one fourth of the circumference.

2) Change in operation of the machine from pump to turbine by only changing the intervals of opening of the four circuits, hence without any change in the internal components.

3) Identical operation of the machine with change in direction of rotation of the crankshaft since said change causes exchange of operation of the two rotors.

4) Capability of identical operation of the machine be exchanging inlet E_(o) with outlet U_(o) of the liquid as demonstrated above.

5) Isolation of the liquid pumped from the external environment particularly useful in the case of pumping of poisonous or overheated liquids.

6) It is also observed that the machine can work with liquid or pasty or solid liquids of the granular type.

7) The capability of changing the velocity of rotation of the crankshaft, obtaining pressures, velocities and powers from very low to very high.

8) The capability of changing the direction of rotation of the crank and obtaining identical values of Q_(o) and P_(o).

9) Limited maintenance costs thanks to the simplicity of the components.

10) The machine with its particular characteristics is designed to solve difficult problems concerning the transmission and use of mechanical power.

11) Broadening of the field of application of the pump and turbine with change in velocity of the crankshaft is possible in a broad interval. 

1. Machine functioning as a pump or turbine and consisting of a mechanism transmitting to a tubular circuits system rotational inertial forces of the periodic type which develop in the liquid contained therein a pressure and a flow with continuous character and including a supporting frame and a system of oscillating means bearing tubular circuits and characterized by being constituted by two identical oscillating rotors with identical frequency and phase differing by 180° with there being fastened on each rotor two identical tubular circuits each of which has an identical interval of opening with duration equal to one fourth of the period T of the rotatory motion of the crankshaft.
 2. Machine in accordance with claim 1 characterized by the simultaneous opening respectively of the two circuits (C₁, C₃) and (C₂, C₄) fastened to two different rotors in order to balance the supporting frame and divide in two equal parts the power developed by the machine.
 3. Machine in accordance with claim 1 characterized in that the length of each active circuit with opening as set forth in claim 1 satisfies the relation I_(o)=Π/2r_(B) (1-4N_(o)) where N_(o) is the number of circumferences used.
 4. Machine in accordance with claim 1 characterized by a closing and opening disk valve whose diameter coincides with the axis of its rotation shaft which rotates perpendicular to the axis of the active circuit with the valve having the characteristic of a rotation reduced by 90° for its own operation and of reduced losses and null moment of the forces parallel to the axis of the circuit.
 5. Machine in accordance with claim 1 characterized by a valve with rectangular cross section and opening and closing door rotating around a lateral shaft with axis perpendicular to the axis of the circuit and with the valve having the characteristic of an angle of rotation of the door variable between 30° and 90° and the disadvantage of a high closing and opening moment of the valve; it is advantageous in case of small flows.
 6. Machine in accordance with claim 1 characterized by the opening and closing of the valves by means of coupling of a rack arranged at one end of the valve control shaft with a rack fastened to the supporting frame and with the operation being facilitated by the use of two racks arranged at the ends of the crankshaft.
 7. Use of the pump in accordance with claim 1 for transport of dangerous liquids, this being facilitated by the absence of outlets in the tubular circuits.
 8. Use of the pump in accordance with claim 1 for transport of pasty, granular or broken solid substances.
 9. Use of the pump in accordance with claim 1 characterized bay transformation of the hydraulic power developed by the active circuits intl mechanical power by using the series of oscillating rotor components, crank connecting rod, and shaft of the cranks. 